Cam drive mechanism
For the conversion of a reciprocatory into a rotary motion or vice versa, a reciprocating member is acting upon at least one cam of a driveshaft. Among the benefits and advantages resulting from the choice of the cam profile, there is the possibility of a single cylinder engine which is full balanced, with respect to forces and moments, and a three-in-line which is balanced as perfectly as the Wankel rotary, i.e. perfect balance not only as regards inertia forces and inertia moments, but also as regards inertia torques. It turns out that the form of the profile of the cam and the location of its axis of rotation, relatively to the axis of the reciprocation are substantially limitless.
This invention solves the known problem of the desmodromic, or positive, control of a reciprocating member comprising a pair of rollers riding on a uni-lobe cam.
By uni-lobe cam is meant a cam whose one rotation corresponds to only one reciprocation of the reciprocating member.
By desmodromic or positive control is meant that if the one roller is in contact with the cam, the other roller is no more than the running tolerance away from the cam.
In the art there are drive mechanisms using multi-lobe cams, as in U.S. Pat. No. 4,545,336 patent or uni-lobe cams as in GB 891,490.
The uni-lobe is simpler, smaller for the same stroke and can use counterweights, fixed on its shaft, for balancing inertia loads.
It is possible for a cam mechanism to employ a second camshaft to bear the thrust loads, or can bear the thrust loads on walls, immovable or rotatable to provide variable compression.
The latter needs not a gearing of high strength/high accuracy/small clearance to connect the cooperating camshafts, is cheaper to make and compact.
The uni-lobe cam must control desmodromicly the reciprocating member in both directions. Unless the necessary cam profile can be defined as strictly as to provide the demanded quality and accuracy of the reciprocation the control is impossible, the cam cannot meet the contemporary demands.
As a roller rolls along a cam, it contacts the cam along the cam profile but the center of the roller travels along its own path which, being the trace of the center, can be called the centers curve.
The centers curve derives from the cam profile and the radius of the roller. Likewise, keeping the center of the roller on the centers curve and moving it along its successive positions, the roller defines the profiles of two cams, one external and one internal. If the axis of a milling cutter follows the centers curve, while removing material from a plate, it is machining the two cams mentioned.
Any point on the centers curve derives the respective point of the cam profile by drawing a line, of length equal to the radius R of the roller, perpedicular to the centers curve at this point, as
In GB 891,490 patent the control of the reciprocation is provided by a uni-lobe cam whose geometry is described in Page 3, lines 50 to 69, and in
The constant breadth cam of US 0020043225 patent application can control the system desmodromicly only if the diameter of the rollers is equal to zero, for reasonable diameter of the rollers the mechanism cannot be desmodromic.
Besides its main cam lobe, the engine of the U.S. Pat. No. 4,493,296,
Compared to groove cams, the use of a camshaft comprising a first external cam, to constrain the reciprocation at one direction, and a second complementary external cam, to constrain the reciprocation at the opposite direction, provides more robust cams of reduced size, easier construction etc. In
The version shown in
In a preferred embodiment the motion converting mechanism of
The shaft (7) has double-disk cams (9) and (10) to allow room for the cam (11) of the shaft (8).
The profile of the cams, i.e. the control surface of the cams is made so that to derive a harmonic reciprocation for the piston rod.
By the mathematical term harmonic it is meant a strictly sinusoidal motion versus the time, i.e. versus the shaft-angle in the case of a single-lobe cam and versus the shaft-angle times the lobe-number for the cases of multi-lobe cams.
The balance of inertia forces and moments for such a reciprocation is simple, even for a single cylinder or a twin, by virtue of a couple of counterweight webs fixed on the shafts, but only in case of single-lobe cams.
The additional merit of the three-in-line of the
Higher order harmonic components can be added to or subtracted from the single-lobe, kidney-shape, cam as shown in
In the multi-lobe cams, of the prior art, the time for one rotation of the multi-lobe cam is longer than the time for a reciprocation of the reciprocating member, thus balance web on them provide no good. Hence, if something makes them in the future desirable, the balance of the engine will necessitate additional counterweight shafts faster than the drive shaft.
Multi-lobe cams impact, as many times as the number of lobes, stronger momentary torques from combustion and even worse torque impacts from inertia, which means as many times stronger impacts for the whole mechanism, gearing included.
FIGS. 32 to 37 show a desmodromic valve control system.
FIGS. 38 to 45 analyze the geometry of the mechanism.
FIGS. 47 to 49 show a mechanism based on a camshaft having two different complementary external cams. Each reciprocating roller cam follower rides on the external surface of its own cam.
In the embodiment of
The cams on the shaft (7) are made as double disk cam (9) and (10), to allow the cams (11) of the shaft (8) to pass through, so that no twisting moment is imparted to the piston assembly.
The camlobes (9) and (10) of the shaft (7) and the camlobe (11) of the shaft (8) rotate. The rollers (5), (6) and (4) on the piston assembly (1) rolls along the periphery of the camlobes, making the piston to reciprocate inside its cylinder. The proper selection of the profiles of the camlobes and of the diameter and arrangement of the rollers on the piston assembly, make the mechanism full desmodromic, as all rollers are kept permanently in contact to the camlobes.
Adjusting means, such as bolting, springs etc, known in the art, may be added to the rod assembly to provide the desirable clearances or preloading between the roller and the lobe.
Unlike a multi-lobe cam, the rotation of the single-lobe cam is of the same order, i.e. frequency, as the reciprocation of the piston, thereby the webs (12) on the counter-rotating shafts suffice for the fill balance of the forces and moments and, as the total kinetic energy of the three harmonically reciprocating members remain constant all along a revolution, there is no inertia torque altogether. The engine of
The even firing, straight four engine of
Replacing the second shaft (8) of
As shown from
E(f)=a+r*sin(f).
A roller having its center on the periphery of the basic curve moves around the curve. Taking a circular disk, like the one shown in upped middle, and subtracting the roller as it rotates around the basic curve periphery, it results the upper right curve and finally the low middle curve. Holding two rollers, like the one used to subtract material from the circular disk, in a distance 2*a from center to center, shown in low middle, and permitting them to move only perpendicularly, the rotation of the cam lobe causes a harmonic reciprocation, along perpendicular axis, of the two rollers assembly, keeping both of them in permanent contact to the cam lobe. In the low right side is shown a groove made in similar way. Using a pair of counter rotating grooves, coaxial or parallel, it can result a reciprocation free from thrust loads.
If the desirable reciprocation is not harmonic, the formula becomes:
E(f)=a+Y(f), where Y(f) is the desirable displacement along the perpendicular axis, relatively to the rotation angle of the cam lobe.
In
E(f+f1)=square root((a+r*sin(f))ˆ2+dˆ2),
with
f1=Arctan((a+r*sin(f))/d),
where d is the offset.
Moving a roller, while keeping its center on the basic curve, it results the cam lobe profile, shown at the middle. In this case the two rollers are in constant distance from each other and reciprocate harmonically as the cam lobe rotates, but they are horizontally offset at 2*d. Two ‘offset’ counter rotating cam lobes are shown in the right side, with a piston assembly keeping all rollers. Again if the harmonic reciprocation is not the desirable one, the formula becomes:
E(f+f1)=square root((a+Y(f))ˆ2+dˆ2),
with
f1=Arctan((a+Y(f))/d).
The above geometrical method apply in the same way for multi lobe cams, for instance two lobe, three lobe etc.
As in the prior art, the space beneath the piston remains available for a second chamber which may serve as a compressor for supercharging etc.
In the following it will be proved that the disclosed solution of the problem of desmodromic or positive control of a reciprocating piston comprising a pair of roller cam followers, by a single cam surface rotating once per reciprocation, is not just one solution but the only possible solution, i.e. it is sufficient and necessary.
In the general case, as shown in
There are only six cases.
1st case: X1 and X2 coincide, R1=R2, O on the coinciding axes.
2nd case: X1 and X2 are not coinciding, R1 equal to R2.
3rd case: X1 and X2 coincide, R1=R2, O outside coinciding axes.
4th case: X1 and X2 coincide, R1 not equal R2, O outside coinciding axes.
5th case: X1 and X2 coincide, R1 not equal R2, O on the coinciding axes.
6th case: X1 and X2 are not coinciding, R1 and R2 are not equal.
Case 1,
Case 2,
E(f+f1)=square root((a+r*sin(f))ˆ2+dˆ2),
with
f1=Arctan ((a+r*sin(f))/d), and the a being a constant. Then, the cam profile CP derives from the centers curve E as an offset by R curve, as shown in
Case 3,
Case 4,
Case 5,
Case 6,
Decreasing until zero the offset d of case 2, it results the case 1, with d=0 and f1=π/2. So the problem of the positive or desmodromic control of a reciprocating piston, having a pair of roller cam followers, by one only uni-lobe cam surface is solved, the solution provided is the only possible while the only limitation is the piston's position function Y(f) to obey in the rule Y(f)+Y(f+π)=constant. The practical application of the method is clear: in the general case, given the piston's position function Y(f) the centers curve E(f) is calculated according the formulas given and then the center of the cutting tool of a milling machine follows the specified centers curve creating the cam.
If the roller, as it moves contacting the cam lobe, is held parallel to itself, then instead of die rolling, a sliding takes place. However, only a small part of the periphery of the roller comes in contact to the cam and the rest periphery of the roller, being free, is not necessary. By machining a pair of cams, one external and one internal, as
The present invention is, of course, in no way restricted to the specific disclosure of the specification and drawings, but also encompasses any modifications within the scope of the appended claims.
Claims
1. A motion converting mechanism comprising a reciprocating member (1) and a rotating member (7);
- said reciprocating member (1) comprising at least two roller cam followers (5) in substantially constant distance from each other;
- said rotating member (7) comprising a cam (9);
- for each rotation of the cam (9) only one reciprocation of the reciprocating member (1) takes place;
- characterized in that:
- the centers of the roller cam followers follow curves, relative to the cam, having an eccentricity E(f) which is related to the displacement Y(f) of the reciprocating member (1) substantially by the formula:
- E(f+f1)=square root ((a+Y(f))ˆ2+dˆ2), with f1=Arctan ((a+Y(f))/d), where f is the rotation angle of the cam, d is half the distance between the axes of reciprocation of the centers of the roller cam followers and a is a constant;
- while Y(f)+Y(f+π)=constant for any f;
- thereby the same cam profile desmodromicly controls the reciprocation in both directions.
2. A motion converting mechanism according claim 1,
- characterized in that:
- the profile of said cam (9) is such that the reciprocation of the reciprocating member (1) is substantially sinusoidal, versus the rotation angle f of the rotating member (7).
3. A motion converting mechanism according claim 1,
- characterized in that:
- the reciprocating member comprises at least one roller (4) riding either on an immovable surface (16) or on a rotating cooperating cam (11) and bearing thrust loads at low friction to improve mechanical efficiency and reliability.
4. A motion converting mechanism comprising a reciprocating member, at least two rotating external cams, not necessarily of the same size or number of lobes, and at least a thrust wall;
- characterized in that:
- the reciprocating member comprises a roller cam follower assembly, trapped among the cams and the thrust wall.
5. A motion converting mechanism according claim 1,
- characterized in that:
- the resulting side loads are substantially carried by the rolling of rollers on angularly displaceable thrust walls in order to provide variable compression ratio.
6. A motion converting mechanism comprising a reciprocating member and a rotating camshaft;
- said camshaft comprising at least a first external cam and a second external cam;
- said reciprocating member comprising a first roller cam follower and a second roller cam follower;
- said first roller cam follower rides on said first cam with its center following a first centers curve relative to the camshaft;
- said second cam follower rides on said second cam with its center following a second centers curve relative to the camshaft;
- characterized in that:
- the first cam and the second cam are complementary in the sense that any line from the center of rotation of the camshaft, intersects the first and the second centers curves in a sequence of four points A, B, C and D with AC=BD=constant and AB=CD.
7. A motion converting mechanism for desmodromic control of reciprocating valves comprising:
- at least a cam having an eccentric groove and at least a cam follower sliding along said eccentric groove in substantially permanent contact to both sides of the groove;
- characterized in that:
- the cam follower is substantially longer than the width of the groove.
Type: Application
Filed: Oct 29, 2004
Publication Date: Apr 12, 2007
Inventors: John Pattakos (Piraeus), Emmanouel Pattakos (Piraeus), Manousos Pattakos (Piraeus)
Application Number: 10/577,165
International Classification: F01B 9/06 (20060101);